Grinding machine



Dec. 22, 1936. w. PEASLEE Er A1.

GRINDING MACHINE Filed Aug. lO, 1934 l2 Sheets-Sheet l Dec, 22, 1936.

W.V PEASLEE ET AL GRINDING MACHINE Filed Aug. l0, 1934 l2 Sheets-Sheet 2 Summa@ Dec. 22, 1936. w. PEASLEE ET AL GRINDING MACHINE l2 Sheets-Sheet 3 Filed Aug. lO, 1934 M NMNII Dec. 22, 1936. w. PEAsLEE Er AL GR INDING MACHINE Filed Aug. 10, 1934 12 Sheets-Sheet 4 A .t f6 mi WZ mi i i ,/J

Dec. 22, 1936. w, PEAsLEE Er AL 2,065,151

GRINDING MACHINE Filed Aug. 10, 1934 12 Sheets-Sheet 5 n N x C n c M M c v/J ./f M M M f Dec. 22, 1936. W, PEASLEE ET AL 2,065,151

GRINDING MACHINE Filed Aug. lO, 1934 12 Sheets-Sheet 6 Stroe wml;

Dec. 22, 1936. W, PEASLEE Er AL 2,065,151

GRINDING MACHINE Filed Aug. l0, 1954 12 Sheets-Shea?l 7 lig J3 if Iig 70 l2 Sheets-Sheet 8 GRINDING MACHINE W. PEASLEE ET AL Filed Aug. lO, 1934 Dec. 22, 1936.

lig 76 f m M m y am w l J\ fm Dec. 22, 1936. W PEASLEE ET AL 2,065,151

GR INDING MACHINE Filed Aug. lO, 1934 12 Sheets-Sheet 9 Dec. 22, 1936. W PEASLEE ET AL 2,065,151

GRINDING MACHINE Filed Aug. lO, 1934 12 Sheets-Sheet l0 MMM,

Dec. 22, 1936. W, PEASLEE ET AL 2,065,151

GRINDING MACHINE Filed Aug. l0, 1934 12 Sheets-Sheet 1l Dec. 22, 1936. W PEASLEE ET AL 2,065,151

GRINDING MACHINE Filed Aug. l0, 1934 12 Sheets-Sheet l2 Patented Dec. 22, 19536 UNITED STATES GmNmNG MACHINE Willetts Peaslee and Lester F. Nenninger, Cincinnati, and Erwin G. Boehm, Norwood, Ohio, assignorsv to Cincinnati Grinders Incorporated, Cincinnati, Ohio, a corporation of Ohio Application August 10, 1934, Serial No. 739,224

21 Claims.

This invention relates to improvements in machine tools and particularly to improvements in grinding machines and the mechanism for controlling the movements and operations of the several units thereof.

The machine illustrated in the drawings is a grinding machine particularly adapted for the grinding or finishing of large diameter rolls such as employed in steel rolling mills. 'I'he particular machine illustrated was designed for operation on the largest types of said rolls which weigh many tons and must have their surfaces provided with a fine finish. Additionally, these rolls must be accurate within minute tolerances, bot-h as to parallelism and concentricity. In order to produce such rolls the machine must be very massive and be accurately controlled and respond to minute adjustments. At the same time and in order to be commercially successful the said rolls must be produced in a minimum of time.

Accordingly, the principal object of the present invention is the provision of an improved precision grinding machine for producing rolls such as above described.

Another object of the invention is the provision of an improved control and operating mechanism for e'ecting and controlling the relative axial movement of the work' adtl or grinding wheel.

Another object of the invention is the provision of improved actuating and control means for a tool or Work slide for effecting the movement of one of said parts relative to the other, that may be preset for manual or automatic control whereby said controls, while being substantially separate and complete within themselves yet have a number of parts or units common to one another, thereby materially reducing the number of elements or units necessary while producing independent actuating and control mechanisms.

A further object of the invention is the provision of actuating and control mechanism as specified in the preceding paragraph and utilizing hydraulic pressure as the actuating medium.

A further object of the invention is the provision of improved means for effecting the relative feed between a tool and work piece, together with means for automatically securing the parts in clamped or locked position except when a feeding movement is to be effected or in progress.

A still further object of the invention is the provision of improved compensating means for finely adjusting the tool and work relative to one another in a feeding direction to take up wheel-wear and other minute variations in the parts.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the accompanying drawings forming a part thereof and it is to be understood that any modifications may be made in the exact structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

In the drawings:

Figure 1 is a front elevation of a grinding machine embodying improvements of this invention.

Figure 2 is a side elevation shown in Figure 1 as seen particularly from the right hand end thereof.

Figure 3 is a top plan view of the machine.

Figure 4 is a longitudinal sectional view as seen substantially from line 4 4 on Figure 3.

Figure 5 is a transverse sectional view through the rear portion of the machine as seen substantially from line 5--5 on Figure 3.

Figure 6 is a fragmentary sectional view through the wheel head as seen from line 5 6 on Figure 3, certain parts being omitted to more clearly show the construction.

Figure 7 is a fragmentary sectional view, similar lto Figure 6, taken through a plane to the vleft of the plane of Figure 6 and illustrating the transverse adjusting mechanism.

Figure 8 is a view, partly in section and partly in elevation, as will be seen on line 8-8 on Figure 3.

Figure 9 is a fragmentary view as seen from line 9-9 on Figure 8.

Figure 10 is a sectional view through the cambering bar adjusting mechanism as seen from line lll-ill on Figure 8.

Figure 11 is a sectional view taken longitudinally of the spindle as on line I I--i I on Figure 3.

Figure 12 is a fragmentary horizontal sectional view of the wheel feed mechanism as seen on line l2-I2 on Figure 5.

Figure 13 is a sectional view through the cambering bar adjusting mechanism as seen from line |3-I3 on Figure 8.

Figure 14 is a fragmentary sectional view through the valve block as seen from line H-l on Figure 3.

Figure 15 is a transverse sectional view through the valve actuating mechanism and is in effect a continuation of section Iii-I4.

Figure 16 is a staggered sectional view looking in the direction of the arrows on line Iii- I6 on Figure l5 with the bearings of the shafts and rods shown in cross section.

Figure 17 is a horizontal fragmentary sectional a portion of Figure 16 as seen from line I'8-I8 thereon.

' Figure 19 is a transverse sectional view through the valve actuating mechanism as seen from line |9-I9 on Figure 14.

Figure 20 is a sectional view taken on Iline 29--20 on Figure 6.

Figure 21 is a fragmentary sectional view taken on line 2 I-2I on Figure 16.

Figure 22 is,a sectional view taken 22--22 of Figure 19.

Figure 23 is a staggered sectional view taken on line 23'23 on Figure 1.9.

Figure 24 is a fragmentary sectional view through the valve block as seen from'line 24-24 on Figure 19.

Figure 25 is a sectional view through the control valve housing for the transverse or cross feed slide as seen from line 25-25 on Figure 31.

'Figure 26 is a view similar to Figure 25, but taken through a plane spaced from that of Figure 25 as on line 25--25 on Figure 31.

Figure 27 is a view similar to that of Figures 25 and 26 but taken through a plane spaced from that of Figure 26 as on line 26--26 on Figure 31.

Figure 28 is a diagrammatic view of the hydraulic circuit involved in the invention.

Figure 29 is a sectional view through the slide locking mechanism as seen from line 29-29 on Figure 5.

Figure 30 is a sectional view through one of the valves as seen from line 30--38 on Figure 24.

Figure 31 is a plan view of the control mechanism for the transversely shiftable slide.

Figure 32 is a plan view of a portion of Figure 16 as seen from line 32-32 thereon.

'I'hroughout the several views of the drawings similar reference characters are employed to denote the same or similar parts.

A machine of the present invention comprises two independent assemblies, one for supporting and driving the work while the other supports the tool or grinding wheel. Each assembly includes a mainv supporting bed 30 and` 3| respectively mounted on a separate cementitious support 32 and 33. -As seen in Figure A2 the supports are of different elevation, the surface of the support 33 being considerably below the surface of the support 32 and-additionally being in the form of an island entirely surrounded by a trough 34 which constitutes the coolant tank. Each of the beds 30 and. 3| is mounted on a plurality of leveling blocks or jacks 35 spaced at intervals along each sideof the said beds. Extending through each of said leveling jacks is an anchor or fastening on line bolt 36 having its lower end rooted in the cementitious supports 32 and 33. v

The work supporting bed 30' is of a relatively shallow depth and of fabricated or welded construction to which is bolted the flat and inverted V guide ways 31 and 38 supporting for adjustment relative thereto a taiistock 39 and journal rests 40 and 4|. The journal rests 40 and 4| are adapted to support the journals 42 of the work piece 43 here shown as a roll of the type used in steel and paper mills. Beyond the guide ways 31 and 38 the bed 38 has secured thereto a headstock 44 fromv which projects a center 45 and a driving face plate 46. The face plate 46 is rotatably driven from a motor 41 mounted extraneously of the machine on the cementitious support 32 through a suitable transmission contained in the headstock 44. The headstock center 45 is in axial alignment with a center.48 projecting from a spindle 49 associated with the taiistock 39Nand the said centers 45 and 48 constitute terminal abutments for the work or roll 43. The taiistock 39 is adaptedto be translated on the ways 31 and 38 by a self-supported motor 58 connected through a suitable transmission carried by the headstock to a driving pinion (not shown) connected vwith a .rack carried by the guide way 38. Additionally, the spindle 49 is axially adjustable relative to the taiistock housing 39 by means of a hand wheel 52 mounted on the taiistock 39.

The bed 3| of the tool supporting assembly. similar to the bed 30, is of relatively shallow construction so far as height is concerned and is likewise formed of fabricated or welded construction. Bolted or otherwise secured to the bed 3| are the flat and V ways 53 and 54, see Figure 5, receiving respectively the guides 55 and 56 depending from the translatable slide 51. The slide 51 is of fabricated or welded construction as shown in Figure 5 and supports the grinding wheel, the means for rotating the grinding wheel, all of the means for controlling its translation and the means for effecting and controlling the transverse adjustment oi the grinding wheel as will later be made clear, and in addition provides the operators station which travels therewith during the grinding or tooling operation. Mounted on' the translatable slide 51 is a base plate 58 on which is formed the fiat and V guide ways 59 and 60. Cooperating with said guide ways are the guides 6| and 62 depending from the transversely adjustable slide 63. The transverse slide 63 has provided at its forward end trunnion bearings 64 in which is journaled a trunnion shaft 65 for a tool `carriage 66. The tool carriage 66 is adapted to be manually and automatically oscillated about the axis of the trunnion shaft 65 by means to be described later.

The carriage 66, see Figure 11, provides bearings 61 and 68 in which is rotatably journaled a spindle 69. 'Ihe spindle 69 is provided on its forward end with a tapered nose 16 to which is keyed and clamped a wheel collet 1| to which is in turn secured a grinding wheel 12. The wheel 12 is substantially enclosed by a guard 13 carried by the carriage 66 and is employed to confine the coolant used on the wheel and work. The other or rear end of the spindle 69 is also provided with a tapered nose 14 to which is keyed and clamped a pulley or sheave here shown as of the multiple groove type. The pulley or sheave 15 has trained thereabout a plurality of V belts 16, in turn, see Figure 2, being trained about a driving sheave 11 on the shaft of driving motor 18. The motor 18 is secured to the carriage 66 and partakes of all movements imparted thereto.-

The grinding wheel spindle 69 is adapted to be axially shifted relative to the bearings 61 and 68. For this reason it is provided substantially centrally of its length with an enlarged flange portion 19 on either side of which, encircling the spindle, are the collars 19aI and 8| forming therebetween a circumferential groove 88 receiving the spindle flange 19. The collar 8| has projecting therefrom at diametrically opposite points bosses 82 and 83 and the said collar is surrounded by a second ring 84 through which passes pivot screws 85 and 86 entering the collar or ring 8| through the bosses 82 and 83. The ring 84 is likewise provided with diametrical bosses 81 and 88 which are disposed at right angles to the bosses 82 and 83. Disposed partially around the ring 84 is a yoke member 89 carrying pivot bolts 90 which enter into the second ring bosses 81 and 88. The yoke 89 is .keyed or otherwise secured lto the lower end of a vertically disposed shaft 9| rotatably journaled in a bearing provided by the carriage A66 and a second bearing provided by a housing 92 secured to the carriage 66 above the spindle. The upper end of the shaft 9| projects into 4the interior of the housing 92 and haskeyed thereto a segmental worm wheel 93. Meshing with the teeth of the segmental worm wheel 93 is a worm 94 integral with or secured to a worm shaft 95, see Figure 11. The shaft 95 is rotatably journaled in bearings supplied by the housing 92 and projects be= yond the housing to receive a hand wheel 96. It should be noted at this time, and as will be seen from Figure 1l, that the hand wheel is disposed on the same side of the grinding wheel carriage as the grinding wheel itself, which is adjacent to an operators station on the translating slide 51.

The operation of the spindle reciprocating mechanism is believed obvious since a rotation of the hand wheel 96 in one or the other direction will correspondingly oscillate the Worm segment 93 and thereby the yoke 89. This will tend to shift the rings 8| and 84 axially of the spindle but since there is no lost motion on either side of the spindle flange 19 and the collars or inner ring 19a and 8| the spindle itself will be moved thereby. It should be noted, however,

that in machining the collars or in mounting same on the spindle the abutment faces presented thereby to the said inner or rst ring may not be truly at right angles to the opposed faces of the first or inner ring 8| and since it is held by the yoke and associated mechanisms the spindie may have a tendency to vibrate slightly when the high portions engage one another which is overcome by the double pivoting of the inner and outer rings, permitting them to oscillate about their pivotal mountings while maintaining the spindle in a, definite axial position. It is to be understood that this out of squareness of the parts above mentioned is very minute and even if not compensated for would be invisible to the eye but suicient to possibly interfere with the production of precision work pieces.

As was suggested above, the transverse slide 63 is movable laterally of the rear bed 3| or laterally of the translatable base plate or slide 58. The means for effecting this movement, as shown in the present application, is of the pressure iluid or hydraulic type and it will be noted that this transverse slide is normally clamped or locked against movement except when the slide is being actuated, the clamping of the slide being also eifected by hydraulic means and so interconnected with the traversing means as to be automatically operated both for unclamping the slide prior to movement thereof and then clamping the slide upon cessation of said movement.

The hydraulic mechanism for effecting and controlling the movement of the transverse slide is shown diagrammatically in the left hand portion of Figure 28 and structurally in several other gures and this mechanism will be described as seen in said Figure 28, the diiferent units being structurally described as they are encountered in the diagram. Accordingly, this mechanism comprises a pump 91 driven by a motor 98 located on the translatable slide 51. The pump 91 has extending from one side thereof a suction pipe 99 terminating in a' tank |00 which contains the hydraulic actuating medium, preferably oil. It

should be noted-that the interior of the fabricated translatable slide 51 is utilized as the tank |00. Extending from the other side of the pump 91 is the main pressure pipe or conduit |0| which terminates in the control valve indicated generally in Figure 28 by the reference character |02. Extending from the pipe or conduit |0| is a branch, discharge, conduit |03 containing a relief valve |04 which determines the actuating pressure in the pipe |0| and therefore the hydraulic system.

The control valve unit'l02 is shown diagrammatically in Figure 28 and structurally in Figure 27 and comprises a valve casing or block |05 mounted on the translatable slide 51. The block |05 is provided therein with a bore |06 into which is pressed-a bushing |01 having formed therethrough a plurality of ports |08, |09, ||0, ||2, ||3, ||4, ||5, ||6 and ||1, each set of ports b'eing encircled by a similar circumferential groove ||8 -formed in the exterior of the valve bushing |01. Disposed within the bore in the valve bushing for axial movement relative thereto is a valve member I9 having formed thereon a plurality of piston portions forming between them cannelures |20, |2|, |22, |23 and |24 which connect the several sets of radial ports in different combinations depending upon the position of the valve member ||9 relative thereto.

It is with the ports I0 of the valve bushing |01 I that the other end of the pipe |0| connects, while the ports |08 and l2 have respectively connected therewith branch discharge pipes or conduits |25 and |26 which empty into main discharge pipe or conduit |21 that terminates in the sump or tank |00. The ports |09 have connected therewith one end of a pipe or conduit |28 terminating at its other end at one end of the slide clamping cylinder, indicated generally in Figure 28 by the reference character |29, While the other end of this cylinder is connected by a pipe or conduit |30 with the bushing ports 'Ihe ports ||3 and ||1 are respectively connected through branch pipes or conduits |3| and |32 with a pipe or conduit |33 which terminates at Athe stop-throttle or rate control valve mechanism indicated generally in Figure 28 by the reference character |34. The ports ||4 and ||6 have respectively connected therewith one end of pipes or conduits |35 and |36 respectively terminating at their other ends at opposite ends of the transverse slide actuating piston and cylinder mechanism indicated generally in Figure 28 by the reference character |31. The remaining ports ||5 of the bushing |01 are connected to one end of a pipe or conduit |38 which is connected, intermediate its ends, with the pipe or conduit |28 extending from the clamping cylinder |29 and the pipe |38 terminates at one end of a shuttle Valve mechanism indicated generally in Figure 28 by the reference numeral |39.

The valve member I9 has three positions; the neutral or clamping position shown in Figures 27 and 28 and one position on either side thereof. The mechanism for effecting the operation of the valve is shown in Figures 5, 25, 27 and 31 and comprises the lever |40 shown in Figure 5 and keyed or otherwise secured to a, short shaft or stud |4| oscillatably mounted in a bracket |42 carried by the translatable slide 51. On the other side of the bracket |42 the shaft |4| has keyed or otherwise secured thereto an arm |43 having pivotally connected to its upper or free end the forward end of a link |44. The rear end of the link |44 is pivotally connected to the lower end of a lever |45 fastened to the end of a shaft |46. The shaft |46 is i'ournaled in the walls of a bracket orhousing |41-to which is secured the valve block |06 and which housing contains the actuating mechanism for the several valves utilized in controlling the transverse movement of the transverse slide. As seenin Figures 25, 27 and 31 the shaft |46 interior-1y of the housing |41 has keyed or otherwisesecured thereto a segmental gear |48 and an end carried by the housing |41 and the other end carried by a counterbored sleeve |56 secured to the forward face of the housing |41. Encircling the shaft |55 on each side of the arm |49 is a' spring |51 and |58 respectively abutting on their inner ends the flanges |5| and |52 of thesleeves |53 and |54 and on their outer ends with the housing |41 and the base of the counterbore in the sleeve |56. The springs |51 and |58 exert their yielding force toward one another for normally holding the arm in the central position shown in Figure 25, the movement of the arm |49 as effected by the springs being limited by an enlarged portion |59 on the shaft |55 which is the portion normally straddled by the bifurcated end |50 of the arm. From the' foregoing it will be seen that the lever may be actuated in either direction relative to the axis of the shaft |4|, thereby effecting reverse oscillations of the arm |49 and a compression of one or the other of the springs |51 and |58. At the same time release of the lever |40 will permit the compressed spring to expand and return the parts to their normal position.

The segmental gear |48 has its teeth in mesh y with a gear or pinion |60 fast on a shaft |6|',

which, similar to the shaft |46, is rotatably journaled in the walls of the housing |41 or suitable bearings provided thereby. In addition, the shaft |6|' has pinned or otherwise secured thereto a cam member |6|, on the periphery of which rides a roller |62 rotatably carried by an arm |63. The arm |63 is oscillatable journaled on a pin supported by the housing |41 and has its free or ball end |64 contacting with the valve member ||9. In order to maintain engagement between the Valve member ||9 and the ball end |64 of lever |63, as well as contact between the roller |62 and periphery of cam |6|, the said valve member I9 is yieldably actuated toward the right as seen in Figure 27 by means of a spring |65 abutting on the end of the valve member ||9 and the base of the guard sleeve |66.

From the foregoing it will be lappreciated that depending upon which point of the periphery of the cam |6| is in engagement with the roller |62 will depend theposition of the valve member ||9. As shown in Figure 27, the parts are so related as to hold the valve I9 in its normal clampingposition, thereby imparting no movement to theA transverse slide.

Rotation or oscillation of the cam |6| however, either in a clockwise or counterclockwise direction, from the position shown in Figure 27 effects a,oes,is1

ber |I8 is such that the upper slide is moved in the direction of movement of the lever, that is, movementl of the lever |40 ina clockwise direction or to the right as seen in Figures effects the corresponding movement of theupper slide and therefore the grinding wheel,while reverse movement of the lever |40 reversely moves the said upper slide and grindingl wheel; It should .be noted, however, that the initial movement of the lever |40 and therefore the cam |6| is limited so that the said cam may be moved from the position shown in Figure 27 in either direction only to'the position where the high or the low point |68 or |69 is in contact with the roller |62. In ether words, the initial movement of the handle |40 is limited to the shifting of the valve member ||9 from the position shown in the drawings to either of its extreme operative positions. The handle is-sthere held until the slide is unclamped whereupon the handle may be moved to effect actuation of the slide but the valve ||9 is not further moved because the concentric portions |10 and |1| ofthe cam are at this time riding on the roller |62 without eiecting any further oscillation of the lever |63.

The means for Hunting this initial movement of the handle |40 comprises a mutilated disc |13 having cutaway or relieved portion |14 supplying shoulders |15 and |16 which are adapted to engage with the nose |11 of a latch member |18. The latch member |18 is pivoted intermediate its ends at |19 to an arm |80 integral with and projecting from the-valve block |05. As seen in Figure 25, the latch |18 is engaged on one side of the pivot |19 by a spring pressed plunger |8| and on the other side by a piston valve member |82. As shown in the drawings there is no pressure behind the piston valve |82, wherefore the plunger |8| is holding the-latch |18 in interfering position in order to engage either of the shoulders |15 and |16 depending upon in which direction the shaft |6| is rotated.

Continuing now with the circuit as shown in Figure 28 and with a detailed description of the different units as encountered therein it will be noted that cannelure |2| of the valve member ||9 is connecting pressure conduit |0| with the conduit |30 and therefore the right hand end of the piston and cylinder mechanism |29. This piston and cylinder mechanism is shown' structurally in Figure 5 and comprises a cylinder |83 which also acts as a valve bushing. Disposed within the bore in the cylinder |83 is a piston |84 having extending therefrom a piston rod |85.`

The rod is slidably mounted in a head |86 at one end of the cylinder |83. 'Ihe other end of the cylinder |83 is closed by a second head |81 through which is formed va port |88. Additionally, the cylinder |83 is provided with ports |89, |90, |9| and |92 adapted to be connected with one another in diierent combinations depending upon the position of the piston relative to the cylinder and by the cannelure |93 formed in the piston |84. v

It is with the ports |92 thatthe conduit |30 connects while the port |88 has connected therewith the conduit |28. The port is connected by a conduit |94 with the main discharge conduit |21 while the ports |89 and |9| have respectively connected therewith one end of conduits and |96 respectively terminating in the latch releasing mechanism indicated generally piston I 84 is shifted to the opposite ends of the cylinder |83 by hydraulic pressure, entering the said cylinder by way of conduits |28 and |30. The position of the piston shown in Figure 28 is the transverse slide clamping or locking position and the means for effecting the said clamping or locking of the slide is shown structurally in Figures 5 and 29. This means comprises a cross head |98 secured to the piston rod |85. Pro- Jecting from the cross head is a pin |99 received in the forked end 200 of an arm 20|. `The arm 20| is keyed or otherwise secured to a shaft 202 oscillatably journaled in bearings 203 provided by the base plate 58. Adjacent each end of the shaft 202 it is provided with eccentrics 204 and 205 respectively disposed in the eyes 206 and 201 of draw or clamping bolts 2 08 and 209. Secured to the upper ends vof each clamping\bolt 208 and 209 is an elongated clamping shoe 2|0 and 2||, each including a clamping lug 2|2 respectively cooperating with a flange 2| 3 projecting laterally from either side of the V way 62 of the transverse or upper slide 63.

The clamping and release of the slide will therefore be effected by reverse oscillations of the shaft 202 which in turn is effected by reverse reciprocations of the pistonv |84.

With the parts in the position shown in Figure 28 the flow oi the hydraulic medium oontinuous from the piston and cylinder mechanism through a pipe or conduit 2|4 which is connected at one end with the pipe or conduit |30 and port |92 of the cylinder |83 and at its other end is the latch releasing mechanism |91. The latch releasing mechanism |91 is shown structurally in Figure 25 and comprises a valve bushing 2|5 pressed into a suitable bore formed in the valve block |05. The bushing 2|5 has formed therethrough a plurality of sets of radial ports 2|6, 2|1 and 2|8, each set of ports being connected by a groove 2| 9 formed .circumferentially of the bushing 2|5. Disposed within the bore in the bushing 2|5 is the plunger |82 which has integral therewiththe valve portion 220, also constituting the piston which effects the movement of the plunger |82 for disposing the latch |18 to its inoperative position. The piston or valve portion 220 is provided with a cannelure 22| for connecting the ports 2|1 and 2|8 wheh in the position shown in the drawings.-

The ports 2| 6 and 2|1 of the valve bushing 2|5 have respectively connected therewith the other termini of pipes or conduits |95 and 2|4 extending from the piston and cylinder mechanism |29. 'Ihe remaining ports 2|8 of the bushing 2|5 have connected therewith one end of pipe or conduit 222 terminating at its other end in the shuttle valve mechanism |39.

The flow of the hydraulic medium, as seen in Figure 28, is from the conduit 2|4 through the latch releasing piston-valve mechanism |91 to the conduit 222 and the shuttle valve mechanism |39; clearly shown in Figure 28.

The shuttle valve mechanism |39 comprises a valve bushing 223 having formed therein' ports 224, 225, 226 and 221. Disposed in the bore in the bushing 223 is a shuttle valve member 228 having formed therein a cannelure 229 for connecting, when in the position shown in Figure 28, the lports 225 and 226. It is with the ports 224 dis-- posed at one end of the bushing and therefore on one side of the valve member 228 that the conduit |38 connects, while the ports 221 disposed at the other end of the bushing 223 and therefore on the other side of the valve member 228 has connected therewith one end of the conduit |88 which has its other end connected with the slide clamping piston and cylinder mechanism |28. Connected ywith the ports 225 is one end of a pipe or conduit 230 terminating at the other end in a selector valve mechanism 23| of the means for controlling the operation of the translatable slide which in turn connects with the sump by means later to be made clear. Additionally, thev selector ,valve mechanism 23| provides a back pressure in the conduit 230 which will also be described in detail later. Connected with the remaining ports 226 of the bushing 223 is the pipe or conduit 222 extending from the latch releasing piston mechanism |91.

From'the foregoing it will now be seen that with the upper or transversely movable slide, which carries the grinding wheel, in a normally locked position the pump 91 is short circuited on itself to the sump or tank |00, while at the same time a back pressure is maintained on the fluid in the system. Thisback pressure acting on the clamping piston |84 maintains same in the position shown in the drawings. Assuming now it is desired to shift the grinding wheel and therefore the slide 63 toward the work or to the right as seen in Figure 5 the lever or handle |40 is shifted in this direction. This actuation of the handle |40 is therefore clockwise as seen in Figure 5 which will effect a similar movement of the cam 6|, thereby permitting the roller |62 to ride on the portion of cam rise |61 down to the low point |68. This permits the spring |65 to shift the valve member 9 to the right as seen in the drawings and the movement of this cam continues until the shoulder |16 of the disc |13 engages the nose |11 of the latch |18. The valve member ||9 at this time takes the position with the cannelure |20 connecting the pressure conduit with the conduit |28. The pressure then in conduit |28 simultaneously passes into the cylinder |83 and through conduit |38 to the shuttle valve mechanism |39 and main valve mechanism |02 where it is connected through the cannelure |23 with the pipe or conduit |35. At this particular instant, however, the clamping piston |84is not moved, nor is the piston andcylinder mechanism |31 actuated but instead the shuttle valve member 228 is shifted to its second operative position, that to the right of the position shown in Figure 28. This movement of the shuttle valve member 220 disconnects the conduits 222 y and 230, so that irrespective of whether the line |30 and associate conduits are connected with pressure as when the'valve ||9 is in the position shown in Figure 28 or with exhaust when the valve is laterally displaced, there can be no escape of the actuating medium through check valve 269 to the right hand portion of the system until such time as adequate pressure has been built up in line |30 to shift the clamp into its left hand locking position uncovering port |9| so that the shuttle valve is positively reversely shifted.

With the full pressure now in conduits |38 and |28 acting on the piston |84 it is shifted to its releasing position to the right of that shown in the drawings. At this time the conduits |95, from the latch releasing mechanism |91, and the discharge' conduit |94 are disconnected and instead the piston |84 connects the ports |88 and |89, as shown in Figure 5, thereby connecting the pressure in the conduit 38 with theV conduit |95 and effecting a movement of the piston valve member 220 to the left as seen in Figure 28 or to the right as seen in Figure 25, thereby removing Vshoulder |18.

6 the latch nose |11 from lther-pathY of the disc As was mentioned above, the movement of the valve member ||9 to its operativeY position connects the pressure with the conduit |35 for en'ecting the movement of the slide toward the work.

The piston and cylinder mechanismv 4is shown structurally in Figure '1 and comprises a cylinder 232, closed at one end by a head 233 and at the other end by a head 234. Disposed within the cylinder 232 is a piston 235 having extending therefrom a piston rod 236. The rod 2136 is mounted for sliding movement through a suitable stumng box in the head 233 and has its projecting end connected to a tongue 231 depending from conduit |36 is connected with the pipes or conduits |32 and 33 through the valve cannelure |24 to the 'throttle valve mechanism 134. It will bef seen from Figure 28 that any flow through the exhaust pipes is blocked by the said throttle valve |34; therefore, even though there is pressure now acting on the piston 235, it is not now movable.

' The throttle valve mechanism is shown structurally in Figure 26 and comprises a valve bushing 238 pressed into a suitable bore form'ed in the valve block |05. The bushing 238 lhas formed ltherein a, pair of sets of radial ports 239 and 240, each set being encircled by a similar circumferential groove 24| formed in the exterior of thebushing 238. It is with the ports 239 that the pipe or conduit |33 connects while the ports 240 have connected therewith a branch discharge pipe or conduit 242 emptying into the main discharge conduit |21 and therefore the sump or tank |00. f

Disposed within the bore in the bushing 238 is a valve member 243 having formed therein a reduced portion or cannelure 244 forming at one end a shoulder 245. The shoulder 245 is adapted to be shifted relative to the ports 239 to more or less open said ports and permit a flow therethrough, which is regulated to determine the 'speed at which the piston and cylinder mechanism is to be actuated and therefore the speed at which the grinding wheel is to be moved.

The valve member 243 is normally shifted to' the right by means of a spring 246 disposed Within a socket in the spring guard sleeve 241, the spring abuts at one end the base of the socket and at the other end the adjacent terminus of the valve member 243. The spring 246 holds the saidA valve member 243 against the free or ball end 248 of a lever 249 pivoted at its lower end to the housing |41. In between the ends of the lever 249 it carries a roller 250 riding on the periphery of a cam 256 which extend to the point 251.

25|, pinned or otherwise secured to the cam shaft |6|.

The cam 25| is simultaneously rotated with the cam |6| and mutilated disc |13 but only comes into play after the slide has been released or unclamped. For this reason the cam 25| is provided with a concentric portion 252 extending substantially from a point 253 to a point 254. Extending respectively from the points 253 and 254 the cam 25| is provided with rising portions 255 and The concentric portion 252 has an extent substantially equal to the rising cam portion |61 of the cam |6| and lies within the zone of movement of the shaft |6 as permitted by the shoulders |15 and |16 of the and releasing piston and cylinder mechanism |29, upon release of which the latch is rendered inoperative and the handle |40 permitted to be further actuated; the further actuation of the said handle permitting the movement of the slide and at a rate determined by the amount of movement of the said handle.

.The complete operation of the upper or transversely movable slide is as follows:

Handle |40 is-oseillated in one or the other direction about the pivot shaft |4| for correspondingly rotating the cam shaft |6 and compressing one or the other of the springs |51 or'` |58. The

l said handle is moved to the limit of its movement as determined by the shoulders and |16 of the disc |13 contacting with the latch nose |11. This movement of the handle and therefore the rotation of the cam shaft |6| through the cam |6| shifts the main valve member ||9 to one or the other of its operative positions.

At this time the pressure in the conduit |0| is connected with the conduits |28 and |38 for first shiftingthe shuttle valve member 228 and then the-'piston member |84 to release or unclamp the slide 58. Simultaneously with the connection of the pressure in the conduits |28 and |38 the pressure in |38 is connected with either of the conduits and |36, connecting the remaining conduit with the discharge conduit 33 and throttle valve mechanism |34. As soon as the slide is released o r unclamped the pressure is connected with the latch releasing mechanism, whereupon the handle may be further actuated in the '255 and 256 of the cam 25| are engaging the roller 250 which oscillate the-lever 249 and shift the valve member 243 and the shoulder 245 thereon relative to the ports 239. The uncovering of the ports 239 permit the escape of the fluid through the conduit |33 whereupon the pressure in one of the conduits |35 and |36 effects movement of the slide 63.

During this further movement of the handle |40 one of the springs |51 and |58 is being further compressed or loaded and as soon as there is no pressure on the handle |40 the said spring expands to return the lever to its initial position, thereby stopping further movement'of the parts.

The grinding wheel is adapted to be shifted or translated longitudinally of the rear bed 3| along with the translatable slide 51 by suitable as coupled with the motor 98 for simultaneous 75 `projects into the sump or tank |00. Extending from the other side of the pump 260 is a pressurel conduit 262 from which pipe, or conduit 263, ex-

tends, containing the pressure establishing" or relief valve 264. The pressure pipe or conduit '262 terminates at its other end in a pressure reducing valve mechanism indicated generally in Figure 28 by the reference numeral 265. A

branch conduit 266 extends from the pressure conduit 262 and terminates in a combination stop and manually actuated throttle valve mechanism indicated generally in Figure 28 by the numeral 261. Additionally, the pressure conduit 262 has a branch pipe or conduit 268 extending therefrom which terminates in the selector valve mechanism 23|. VAs shown in Figure 28, the selector valve mechanism is connecting the pipe or conduit 230 with 268 and therefore the pressure conduit 262 and branch pressure conduit 266. It should be noted at this time that the conduit 230 has therein a one way check valve 269 permitting Athe flow of the hydraulic medium as effected by the pump 91 through the system Vabove fully described to and through the pipe or conduit 230 and into the conduit 268 while preventing a reverse flow of the medium as would be effected by the pump 260. Since, however, and as will now be explained the resistance to llow through the pipes or conduits 262 and 266 is much less thanthe pressure of the pump 91 in the conduit 230 there is no tendency of the ow through pipe or conduit 268 into the pipe or conduit 230. The valve mechanism 261 by-passes both pumps 91 and 260 to the sump or tank |00 but creates a slight back. pressure in the system.

'I'he stop and manually actuable throttle valve mechanism 261 is shown structurally in Figure 24. As there shown, this valve mechanism comprises a valve block 210 into which is pressed a valve bushing 21| having formed therethrough a plurality of sets of radial ports 212, 213, 216, 215 and 215', each set of ports being encircled by a similar circumferential groove 216 formed in the exterior of the bushing 21|. Disposed within the bore in the bushing 21| is the valve member 211 having formed thereon piston portions 218, 219 and 280. Between the piston portions 218 and 219 the valve member is provided with a reduced portion 28| forming a cannelure, and additionally projecting from the piston portion 219 into the cannelure is a collar 282 slightly less in diameter than the piston portion 219 and adapted tc form a restricted orice 283 between itself and the ports 214. Between the piston portions 219 and 280 the valve member 211 is provided with a reduced portion 284, which however is only slightly less in diameter than the piston portions and forming thereby a restricted orifice 285. It should be noted that the ports 215 are relatively narrow slots which cooperate with the restricted orifice or passage 285 in controlling the rate of flow of the medium therethrough and determine the rate of movement of the slide as will later be made clear.

As seen in Figure 28 the ports 213 have connected therewithv the branch pressure conduit 266, while the ports 214 and 215' are connected with the pipe or conduit 286 emptying into the main return conduit 281, in turn emptying into the tank or sump |00. The ports 215 have connected therewith one end of a pipe or conduit 286 which terminates at its other end in the selectorvalve mechanism 23| while the remaining ports 212 are connected with one end of a pipe or conduit 289 terminating in the reversing valve mechanism indicated generally in Figure 28 by the reference numeral 290. With the valve member 211 in the position shown the flow from the pumps 91 and 260 is respectively through the mechanism for the transversely shiftable slide to the pipe 230, selector valve mechanism 23| and pipes-or conduits 268 and 262 to the pipe or conduit 266, while the flow from theepump 260 is through the pipe or conduit 262 to the pipe or' conduit 266. The flow from the pipe or conduit -266 is through the ports 213, cannelure 28|, restricted orifice 263, ports 214 and pipes or conduits 266 and 281 to the sump |00, the restricted orifice 283 slowing down the iiow to an extent to establish the back pressure-in the systems.

The stop and throttle valve mechanism 261 has two functions, o'ne for effecting the complete stopping of the i'low in the translating system and the second function for controlling the rate of translation when the translatable slide is manually actuated. For this purpose the said valve mechanism is shifted to the left, as seen in the drawings, both manually and by power means. The manual means for eiecting the movement of the valve will be disclosed now and the power means later. Accordingly, the valve member 211 has its outer end contacting with the ball end 29| of a lever 292 carried by a sleeve 293 loosely journaled on a shaft 294 carried by the walls of a casing 295 secured to one face of the valve block 210. Additionally, the sleeve 293 has depending therefrom asecond arm 296 which has its ball end 291 contacting with one end of a rod 298 slidably mounted in a bearing 299 supplied by a second casing or housing 300 which contains the the plunger 298, see Figure 21, contacts with the ball end 30| of a lever 302 oscillatably mounted on a stud 303 projecting from one wall of the control mechanism casing 300. The lever 302 rotatably carries intermediate its ends a roller 304 contacting on the periphery of a heart shaped cam 305. The roller 304 is held in contact with the cam 305 by means of a spring 306, see Figure 24, abutting on one end with the valve ,member 211 and on the other end with a plug 301 which closes the bore through the valve bushing 21 The cam 305 is adapted to be actuated, that is, oscillated in opposite directions from the position shown in Figure 21 but in each instance the valve member 211 is correspondingly shifted, that is, to the left, as seen in the drawings. For this reason the cam is substantially heartshaped, that is, its periphery 308-309 correspondingly rises from the low point 3|0 to the high point 3||. The initial movement of the cam 305 closes olf the ports 214 and opens the ports 212 to direct the pressure to the reversing valve mechanism 290 and then opens the ports 215 to permit the movement of the translating slide at a speed determined by the opening or closing of the ports 215 by the piston portion 219, all as will be more clearly described later.

The means for rotating the'cam 305 is shown in Figures 15, 16 and 21 and comprises a lever 3|2 pivotally mounted at 3|3, for oscillation in a plane from left to right as seen in Figure 16, on a carrier member 3|4. The carrier member 3M is oscillatably mounted on a rod 3|5 for oscillation in a plane at right angles to the plane of oscillation of the lever about the pivot 3|3. From .this it will be seen that the lever is movable from the left to right in Figure 16 as well as toward and y valve actuating mechanism. The inner end of from-the observer of 'this view. These paths of .Disposed within'the bore in the bushing 333 movement of the lever 3 |2 are dened by a'plate 565 secured to the housing 300 above thelever 3|2 and having `formed thereon a-T slot made. up

of branches 586 and 581 through which the said lever projects, see Figure 32. It is the movement of the lever through slot 586 vwhich eiects the oscillation of the cam 305 and for this purpose the A carrier 3|4 has integral therewith a segmental gear A3||i having its teeth meshing with a pinion 3|0 formed on a shaft 3|9. The shaft 3| 9 is oscillatably mounted in a bearing 320 supplied by one wall of 'the'casing 300 and a second bearing 32| provided by the upstanding lug 322. vIt is to the pinion shaft 3| 3 that the cam-305 is secured, wherefore any motion imparted to said shaft correspondingly actuates thecam 305 and\s\hifts the valve.

It should be vnoted at this time that the valve block 210 and its casing 295 and the adjacent valve actuating control mechanism casing 300 are carried by the uppersurface of the translatable slide 51 within convenient reach of the operator. The actuating handle or lever 3|2 is so positionedl with respect to the slide and the operator that its movement to rotate the cam 305 indicates the direction of movement in which the slide `will be translated. It should also be noted that therate of translation of the slide will depend upon how far in either direction the handle 3|2 is shifted since the amount of movement of the handle 3|2 will determine which point on the periphery 308-309 of the cam 305 is controlling the posi- A tion of thevalve member 211 and therefore how rapidly the hydraulic medium is permitted to escape from the ports 215.

The holder or carrier 3|4 has integral therewith al yoke 323, see Figure 16, which straddles a shaft 324. Surrounding the shaft and disposed on each side of the yoke and contacting therewith are washers 325 and 326, each forming the inner abutment for springs 321 and 328 which in turn respectively abut on their cuter ends with collars 329 and 330. As will be seen from Figure 15 the collars 329 and 330 are respectively spaced from bearing lugs 33| and 332 in which respectively are slidably mounted studs projecting respectively from-collars 329 and 330. c

'I'he purpose for thismechansm is to return the handle or lever 3 I 2 to a stopping position upon release thereof, and operates in the same manner as a similar mechanism described above in connection with the handle |40. It should be noted, however, that the los't motion or space between the collars 329 and 330 and the bearing lugs is to y'permit the shifting of the valve member 211 to an open or starting position, that is with the ports 214 closed and the ports 212 open before the opening of the ports 215. This movement of the valve member 211 is utilized in oonnection with the automatic translation of the slide as will later be described.

The reducing valve 265 is shown structurally in Figure 22 and comprises a valve bushing 333 pressed into a bore in the valve block 210. The bushing 333 has formed therethrough a plurality of sets of radial ports 334, 335 and 336, each set being encircled by a similar circumferential groove 331. As seen in Figure 28 it is with the ports 336 that the pressure conduit 262 connects, While the ports 334 and 335 have respectively connected therewith one end of pipes or conduits 338 and 339 which terminate at their other ends in the pilot valve mechanism indicated generally by the numeral 340. t

-sections 356 and 358'.

conduit 339. The valve member 34| is provided axially thereof, through the piston portion 343, with a bore 346 which is intercepted by a trans- -verse bore 341 formed in the reduced portion 344 ofthe valve member. At its outer end the axial bore34| empties intoa chamber 348 formed i in tht.r bushing 333 at this end of the valve, the

said chamber 348 being completed or closed by Aa plug 349 screwed into the valve bushing.

'I'he valve member 34| is adapted to be actuated toward the rightpas seen `in the drawings, for opening the ports 336 by yielding means. For this purpose the bushin 333 is provided with an enlarged counterbore350 in which are disposed spring cups 35| and 352 respectively abutting the-adjacent end of piston valve member 34| and a plug 353 which closes the outer end of the counterbore..350. A spring 354 is provided and has 4one end seated in theA cup 35| and the other end seated in a cup 352, the spring beingV of the expanding `type for shifting the valve member 34| as above indicated toward the right.

The pilot valve mechanism 340 is shown structurally in Figure 14 and comprises a valve bushing 355 pressed into a bore in the valve block 210, which bushing is in effect formed in three parts 356, 351 and 358, the outer portions356 and `358 having relatively Vsmall bores therethrough, while the central portion 351 is provided with a relatively enlarged bore 359. It should be noted, however, that when the bushing portions are placed in the bore in the valve block 210 they are in absolute axial alignment. Considering the bushing as a whole it is provided therethrough with a plurality of radial ports 360, 36|, 362, 363 and 364, each set of ports being encircled by a similar circumferential groove 365 formed in the exterior of the bushing.

Disposed within the aligned bores of the bushing sections is a valve member 366 having piston portions 361 and 368 thereon adapted respectively to be disposed in the bores in the bushing Additionally, the valve member 366 is provided with an enlarged collar or piston portion 369 disposed within the enlarged bore in the central bushing section '351. It should be noted that the piston portions 361, 368 and 369 relatively closely hug the walls of the bore to prevent any leakage past them; Piston portions 361 and 369 are connected to one another by a reduced stem portion 310 of a diameter less than the diameter of the piston portion 361, but suiiiciently spaced from the wall of the bushing bore to permit a complete opening of the ports 363 and 364 when lying thereunder. The piston portions 368 and 369 are also connected by a stem portion 31| of a diameter likewise less than the diameter of the piston portion 368 for fully opening the ports 360 and 36| when lying thereunder. l

From the description thus far it will be noted that there are provided within the enlarged bore 359 of thebushing 351 chambers 312 and 313 lying respectively on the right and left hand sides of the enlarged'piston portion 369 which, 

